US20130189139A1 - Valveless reciprocating compressor - Google Patents
Valveless reciprocating compressor Download PDFInfo
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- US20130189139A1 US20130189139A1 US13/354,263 US201213354263A US2013189139A1 US 20130189139 A1 US20130189139 A1 US 20130189139A1 US 201213354263 A US201213354263 A US 201213354263A US 2013189139 A1 US2013189139 A1 US 2013189139A1
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- Prior art keywords
- piston
- discharge port
- compression cylinder
- fluid
- piston assembly
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- 230000006835 compression Effects 0.000 claims abstract description 143
- 238000007906 compression Methods 0.000 claims abstract description 143
- 239000012530 fluid Substances 0.000 claims description 184
- 230000007423 decrease Effects 0.000 claims description 20
- 230000001965 increasing effect Effects 0.000 description 12
- 230000003247 decreasing effect Effects 0.000 description 10
- 238000012423 maintenance Methods 0.000 description 10
- 238000000034 method Methods 0.000 description 7
- 230000000712 assembly Effects 0.000 description 6
- 238000000429 assembly Methods 0.000 description 6
- 230000001419 dependent effect Effects 0.000 description 6
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 4
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 4
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 239000003570 air Substances 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 229910002092 carbon dioxide Inorganic materials 0.000 description 2
- 239000001569 carbon dioxide Substances 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000002708 enhancing effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 239000003345 natural gas Substances 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
- F04B53/121—Valves; Arrangement of valves arranged in or on pistons the valve being an annular ring surrounding the piston, e.g. an O-ring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
- F04B53/122—Valves; Arrangement of valves arranged in or on pistons the piston being free-floating, e.g. the valve being formed between the actuating rod and the piston
Abstract
Description
- The present invention relates generally to reciprocating machinery, such as reciprocating compressors. More particularly, the present invention relates to a valveless reciprocating compressor.
- This section is intended to introduce the reader to various aspects of art that may be related to various aspects of the present invention, which are described and/or claimed below. This discussion is believed to be helpful in providing the reader with background information to facilitate a better understanding of the various aspects of the present invention. Accordingly, it should be understood that these statements are to be read in this light, and not as admissions of prior art.
- A reciprocating compressor is a positive-displacement device, which utilizes a motor to drive one or more pistons via a crank shaft and connecting rods. Each piston reciprocates back and forth in a compression cylinder to intake a process fluid (e.g., natural gas, air, carbon dioxide, etc.) into a chamber, compress the process fluid within the chamber, and exhaust the process fluid from the chamber to a desired output. In certain reciprocating compressors, valves may be used to control the flow of the process fluid into and out of the chamber. However, valves possess inherent operational inefficiencies. In addition, valve maintenance significantly increases the costs associated with operating the compressor.
- These and other features, aspects, and advantages of the present invention will become better understood when the following detailed description is read with reference to the accompanying drawings in which like characters represent like parts throughout the drawings, wherein:
-
FIG. 1 is a perspective view of an exemplary reciprocating compressor in accordance with an embodiment of the present invention; -
FIG. 2 is a cross-sectional view of the exemplary reciprocating compressor ofFIG. 1 , illustrating internal components of the reciprocating compressor; -
FIG. 3 is a cross-sectional view of an embodiment of a reciprocating compressor having a flow control member configured to selectively block an intake port and a discharge port; -
FIG. 4 is a cross-sectional view of the reciprocating compressor ofFIG. 3 , illustrating movement of a piston assembly relative to a compression cylinder; -
FIG. 5 is a cross-sectional view of another embodiment of a reciprocating compressor having a piston configured to selectively block an intake port, and a flow control member configured to selective block a discharge port; -
FIG. 6 is a cross-sectional view of the reciprocating compressor ofFIG. 5 , illustrating movement of a piston assembly relative to a compression cylinder; -
FIG. 7 is a cross-sectional view of a further embodiment of a reciprocating compressor having a piston configured to selectively block an intake port and a discharge port; and -
FIG. 8 is a cross-sectional view of the reciprocating compressor ofFIG. 7 , illustrating movement of the piston relative to a compression cylinder. - One or more specific embodiments of the present invention will be described below. In an effort to provide a concise description of these embodiments, all features of an actual implementation may not be described in the specification. It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions must be made to achieve the developers' specific goals, such as compliance with system-related and business-related constraints, which may vary from one implementation to another. Moreover, it should be appreciated that such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure.
- When introducing elements of various embodiments of the present invention, the articles “a,” “an,” “the,” “said,” and the like, are intended to mean that there are one or more of the elements. The terms “comprising,” “including,” “having,” and the like are intended to be inclusive and mean that there may be additional elements other than the listed elements. Moreover, the use of “top,” “bottom,” “above,” “below,” and variations of these terms is made for convenience, but does not require any particular orientation of the components.
- Embodiments of the present disclosure may substantially increase operational efficiency of a reciprocating compressor by providing a piston assembly configured to selectively block an intake port and a discharge port via movement of the piston assembly within a compression cylinder. For example, in certain embodiments, a reciprocating compressor includes a compression cylinder having an intake port and a discharge port. The compressor also includes a piston assembly disposed within the compression cylinder. The piston assembly is configured to successively block the intake port, to compress a fluid within an interior volume of the compression cylinder, and to discharge the fluid through the discharge port upon movement of the piston assembly in a first direction. In addition, the piston assembly is configured to successively block the discharge port, to decrease a pressure of the fluid within the interior volume, and to intake additional fluid into the interior volume through the intake port upon movement of the piston assembly in a second direction, opposite the first direction. Because the intake and discharge ports are selectively blocked by the piston assembly, valves (e.g., check valves), which may otherwise be used to control fluid flow through the ports, are obviated. As a result, operational costs associated with valve maintenance may be substantially reduced or eliminated. In addition, because the piston assembly does not interfere with flow through the ports, the efficiency of the reciprocating compressor may be significantly enhanced, as compared to configurations that employ valves which may partially block the ports while in the open position.
- Turning now to the figures, an exemplary
reciprocating compressor 10 is illustrated inFIG. 1 . In the presently illustrated embodiment, thereciprocating compressor 10 includes a pair ofcompression cylinders 12 coupled to aframe 14. A variety of internal components may be disposed within thecompression cylinders 12 and theframe 14 to enable compression of fluids introduced into thecompression cylinders 12. For example, in certain embodiments, thereciprocating compressor 10 may be utilized to compress natural gas. However, in other embodiments, thereciprocating compressor 10 may be configured and/or utilized to compress other fluids, such as air, carbon dioxide, or nitrogen, among others. - A mechanical power source or
driver 16, such as a combustion engine or an electric motor, may be coupled to the reciprocatingcompressor 10 to provide mechanical power to the various internal components to enable compression of the fluid within thecompression cylinders 12. To facilitate access to such internal components, as may be desired for diagnostic or maintenance purposes, openings in theframe 14 may be provided and selectively accessed viaremovable covers 18. Further, thecompression cylinders 12 may also include apiston assembly 20. As discussed in detail below, eachcompression cylinder 12 includes an intake port and a discharge port. Thepiston assembly 20 disposed within thecompression cylinder 12 is configured to block the intake port upon movement of the piston assembly in a first direction. Thepiston assembly 20 is also configured to block the discharge port upon movement of thepiston assembly 20 in a second direction, opposite the first direction. Because the intake and discharge ports are selectively blocked by thepiston assembly 20, valves (e.g., check valves), which may otherwise be used to control fluid flow through the ports, are obviated. As a result, operational costs associated with valve maintenance may be substantially reduced or eliminated. In addition, because the piston assembly does not interfere with flow through the ports, the efficiency of the reciprocating compressor may be significantly enhanced, as compared to configurations that employ valves which may partially block the ports while in the open position. -
FIG. 2 is a cross-sectional view of the exemplaryreciprocating compressor 10 ofFIG. 1 , illustrating internal components of the reciprocatingcompressor 10. In the presently illustrated embodiment, theframe 14 of the exemplary reciprocatingcompressor 10 includes a hollow central body orhousing 22 that generally defines aninterior volume 24 within which various internal components may be housed, such as acrank shaft 26. In one embodiment, thecentral body 22 may have a generally curved or cylindrical shape. It should be noted, however, that thecentral body 22 may have other shapes or configurations in accordance with the disclosed embodiments. - In operation, the
driver 16 rotates thecrank shaft 26 supported within theinterior volume 24 of theframe 14. In one embodiment, thecrank shaft 26 is coupled tocrossheads 30 via connectingrods 28 andpins 32. Thecrossheads 30 are disposed withincrosshead guides 34, which generally extend from thecentral body 22 and facilitate connection of thecompression cylinders 12 to the reciprocatingcompressor 10. In one embodiment, thereciprocating compressor 10 includes twocrosshead guides 34 that extend generally perpendicularly from opposite sides of the central body orhousing 22, although other configurations may be used. The rotational motion of thecrank shaft 26 is translated via the connectingrods 28 to reciprocal linear motion of thecrossheads 30 within thecrosshead guides 34. - The
compression cylinders 12 are configured to receive a fluid for compression. In the illustrated embodiment, thecrossheads 30 are coupled topistons 36 disposed within thecompression cylinders 12 viapiston rods 38. The reciprocating motion of thecrossheads 30 enables compression of fluid within thecompression cylinders 12 via thepistons 36. Particularly, as thepiston assembly 20 is driven forwardly (i.e., outwardly from the central body 22) into acompression cylinder 12, apiston 36 of thepiston assembly 20 forces the fluid within the cylinder into a smaller volume, thereby increasing the pressure of the fluid. Further forward movement of thepiston assembly 20 unblocks a discharge port, thereby enabling compressed fluid to exit thecompression cylinder 12. Thepiston assembly 20 may then stroke backward, thereby unblocking an intake port. Consequently, additional fluid may enter thecompression cylinder 12 through the intake port for compression in the same manner described above. Because the intake and discharge ports are selectively blocked by the piston assembly, valves (e.g., check valves), which may otherwise be used to control fluid flow through the ports, are obviated. -
FIG. 3 is a cross-sectional view of an embodiment of areciprocating compressor 10 having a flow control member configured to selectively block an intake port and a discharge port. As illustrated, thecompression cylinder 12 includes anintake port 40 and adischarge port 42. Theintake port 40 is fluidly coupled to aninlet 44 via aninternal passage 46 through thecompression cylinder 12. In operation, theinlet 44 receives a flow offluid 48, which is routed to theintake port 40 via theinternal passage 46. While theintake port 40 is fluidly coupled to theinlet 44 via aninternal passage 46 in the illustrated embodiment, it should be appreciated that alternative embodiments may utilize an external passage, or a combination of internal and external passages, to couple theinlet 44 to theintake port 40. - In the illustrated embodiment, the
discharge port 42 is fluidly coupled to anoutlet 50 via aninternal passage 52 and anexternal passage 54. As discussed in detail below, thecompressor 10 expels compressedfluid 56 through thedischarge port 42. The fluid then flows through theinternal passage 52 and theexternal passage 54 to theoutlet 50. While thedischarge port 42 is fluidly coupled to theoutlet 50 via theinternal passage 52 and theexternal passage 54, it should be appreciated that in alternative embodiments, thedischarge port 42 and theoutlet 50 may be directly coupled by an internal passage or an external passage, for example. - In the illustrated embodiment, the
piston assembly 20 includes thepiston 36, and aflow control member 58 extending from thepiston 36 in anaxial direction 60. Theflow control member 58 may be integral with thepiston 36, or coupled to the piston 36 (e.g., via fasteners, a welded connection, etc.). As discussed in detail below, theflow control member 58 is configured to block theintake port 40 during at least a portion of a compression stroke to facilitate fluid compression within thecompression cylinder 12. Theflow control member 58 is also configured to block thedischarge port 42 duration at least a portion of an intake stroke to facilitate fluid flow into thecompression cylinder 12. In this manner, the reciprocatingcompressor 10 may cyclically receive a flow of fluid from theinlet 44, compress the fluid within thecompression cylinder 12, and expel the compressed fluid through theoutlet 50. In the illustrated embodiment, thepiston 36 compresses the fluid, and theflow control member 58 controls fluid flow into and out of thecompression cylinder 12. - As illustrated, the
flow control member 58 extends through theintake port 40, and includes aprotrusion 62 that extends outwardly from theflow control member 58 in aradial direction 64. As discussed in detail below, theradial protrusion 62 is configured to selectively block theintake port 40, thereby establishing a substantially sealed volume that facilitates fluid compression. In the illustrated embodiment, theflow control member 58 includes aseal 66 disposed about theradial protrusion 62. Theseal 66 is configured to substantially block fluid flow through theintake port 40 while theradial protrusion 62 is aligned with theintake port 40. As will be appreciated, theseal 66 may include a Babbitt seal, a labyrinth seal, a brush seal, and/or a ring seal, for example. - In addition, the
flow control member 58 includes aninternal passage 68 extending from aninterior volume 70 of thecompression cylinder 12 to anorifice 72 in anexterior surface 74 of theflow control member 58. As discussed in detail below, theflow control member 58 is configured to block thedischarge port 42 while theorifice 72 is offset from thedischarge port 42, and to facilitate flow through thedischarge port 42 when theorifice 72 is aligned with thedischarge port 42. To facilitate fluid flow from theinternal volume 70 to theinternal passage 68, theflow control member 58 includesmultiple holes 76 extending in theradial direction 64 from theinternal volume 70 to theinternal passage 68. As will be appreciated, the number, size and/or shape of theholes 76 may be particularly selected to provide a desired fluid flow into theinternal passage 68 while maintaining the structural integrity of thepiston assembly 20. - In the illustrated embodiment, the
flow control member 58 includes aseal 78 disposed about theexterior surface 74 of theflow control member 58 on opposite axial sides of theorifice 72. Theseal 78 is configured to block fluid flow from theinternal passage 68 until theorifice 72 is aligned with thedischarge port 42. Theseal 78 is also configured to facilitate fluid flow from theorifice 72 to thedischarge port 42 while the orifice and discharge port are aligned. As will be appreciated, theseal 78 may include a Babbitt seal, a labyrinth seal, a brush seal, and/or a ring seal, for example. In the illustrated embodiment, thepiston 36, theflow control member 58, theradial protrusion 62, and theseals piston 36, theflow control member 58, theradial protrusion 62, and theseals - In operation, the
piston assembly 20 is configured to compress fluid within thecompression cylinder 12 via cyclical movement in theaxial direction 60. For example, as thepiston assembly 20 is driven to move in a firstaxial direction 80, theseal 66 contacts aninner surface 82 of theintake port 40, thereby blocking fluid flow into theinterior volume 70. While theorifice 72 is not aligned with thedischarge port 42, a substantially sealed volume is established, which includes theinterior volume 70 and theinternal passage 68. As thepiston assembly 20 continues to translate in thedirection 80, the size of the substantially sealed volume decreases as thepiston 36 is driven toward aninterior surface 83 of theinternal volume 70. Accordingly, the pressure of the fluid within the substantially sealed volume progressively increases. Once theorifice 72 aligns with thedischarge port 42, thepressurized fluid 56 flows through thedischarge port 42 toward theoutlet 50. - Once the
piston assembly 20 has reached the end of the compression stroke, thepiston assembly 20 is driven in the oppositeaxial direction 84 to facilitate additional fluid flow into theinterior volume 70. For example, as thepiston assembly 20 is driven to move in the secondaxial direction 84, theorifice 72 becomes offset from thedischarge port 42. As a result, theseal 78 substantially blocks fluid flow through thedischarge port 42. Furthermore, while theseal 66 is in contact with theinner surface 82 of theintake port 40, a substantially sealed volume is established, which includes theinterior volume 70 and theinternal passage 68. As thepiston assembly 20 continues to translate in thedirection 84, the size of the substantially sealed volume increases as thepiston 36 is driven away from theinterior surface 83 of theinternal volume 70. Accordingly, the pressure of the fluid remaining within the substantially sealed volume progressively decreases. Once theseal 66 is offset from theinner surface 82 of theintake port 40, the reduced fluid pressure within theinterior volume 70 draws additional fluid 48 from theinlet 44 through theintake port 40 and into theinternal volume 70. Once thepiston assembly 20 reaches the end of the intake stroke, thepiston assembly 20 is driven in the firstaxial direction 80, and the process repeats. - In the illustrated embodiment, the reciprocating
compressor 10 includes a double-actingpiston assembly 20 configured to compress fluid within afirst side 85 of thecompression cylinder 12 while receiving fluid into asecond side 87 of thecompression cylinder 12. In this configuration, movement of thepiston assembly 20 in the firstaxial direction 80 compresses fluid within thefirst side 85 of thecompression cylinder 12, and receives fluid into thesecond side 87 of thecompression cylinder 12. Conversely, movement of thepiston assembly 20 in the secondaxial direction 84 compresses fluid within thesecond side 87 of thecompression cylinder 12, and receives fluid into thefirst side 85 of thecompression cylinder 12. As illustrated, thepiston assembly 20 includes two flow control members configured to control fluid flow within respective volumes of thecompression cylinder 12. The firstflow control member 58 is configured to control fluid flow within afirst volume 86 adjacent to afirst side 88 of thepiston 36. Similarly, a secondflow control member 90 is configured to control fluid flow within asecond volume 92 adjacent to asecond side 94 of thepiston 36. - In operation, as the
piston assembly 20 moves in thedirection 80, the firstflow control member 58 successively blocks theintake port 40, drives thepiston 36 to compress fluid within thefirst volume 86, and discharges the fluid through thedischarge port 42. In addition, the secondflow control member 90 successively blocks thedischarge port 42, drives thepiston 36 to decrease fluid pressure within thesecond volume 92, and receives additional fluid into thesecond volume 92 through theintake port 40. Conversely, as thepiston assembly 20 moves in thedirection 84, the firstflow control member 58 successively blocks thedischarge port 42, drives thepiston 36 to decrease fluid pressure within thefirst volume 86, and receives additional fluid into thefirst volume 86 through theintake port 40. In addition, the secondflow control member 90 successively blocks theintake port 40, drives thepiston 36 to compress fluid within thesecond volume 92, and discharges the fluid through thedischarge port 42. Because the reciprocatingcompressor 10 outputs compressed fluid with each stroke, the flow rate of compressed fluid may be greater than compressors employing single-acting piston assemblies having a single flow control member. While the illustrated embodiment employs a double-actingpiston assembly 20 to provide an increased flow of compressed fluid, it should be appreciated that alternative embodiments may employ single-acting piston assemblies. - Because the
intake port 40 and thedischarge port 42 are selectively blocked by thepiston assembly 20, valves (e.g., check valves), which may otherwise be used to control fluid flow through the ports, are obviated. As a result, operational costs associated with valve maintenance may be substantially reduced or eliminated. For example, to service a valved compressor (e.g., to replace valve springs, to replace valve stems, etc.), the compressor may be deactivated and disassembled. The worn components may then be replaced and/or repaired, and the compressor reassembled. In certain compressor configurations, such valve maintenance may be performed every three to six months, for example. As a result, valve maintenance may result in increased operational costs, and prolonged compressor unavailability. Because the illustrated embodiment obviates the valves, compressor maintenance costs may be significantly reduced, while enhancing compressor availability. Furthermore, because thepiston assembly 20 does not interfere with flow through theports -
FIG. 4 is a cross-sectional view of thereciprocating compressor 10 ofFIG. 3 , illustrating movement of thepiston assembly 10 relative to thecompression cylinder 12. As illustrated, theseal 66 of the firstflow control member 58 is in contact with theinner surface 82 of theintake port 40, thereby establishing a substantially sealed volume, which includes theinterior volume 70 and theinternal passage 68. As thepiston assembly 20 translates in thedirection 80, the size of the substantially sealed volume decreases as thepiston 36 is driven toward theinterior surface 83 of theinternal volume 70. In the illustrated embodiment, the stroke of thepiston rod 38 drives thepiston 36 to translate adistance 96, thereby decreasing the size of the substantially sealed volume by an amount equal to the cross-sectional area of the outerradial portion 97 of thepiston 36 multiplied by thestroke distance 96. As the volume decreases, the pressure of the fluid within the substantially sealed volume progressively increases. Once theorifice 72 aligns with thedischarge port 42, thepressurized fluid 56 flows through thedischarge port 42 toward theoutlet 50. - As will be appreciated, the change in size of the substantially sealed volume is at least partially dependent on the
stroke distance 96, and adiameter 98 of thepiston 36. For example, increasing thestroke distance 96 provides a greater change in the fluid volume, thereby increasing compression. Conversely, decreasing thestroke distance 96 provides a reduced change in the fluid volume, thereby decreasing compression. Furthermore, apiston 36 having alarger diameter 98 establishes a larger sealed volume, while apiston 36 having asmaller diameter 98 establishes a smaller sealed volume. The initial size of the sealed volume defines the fluid volume prior to compression. Consequently, a larger initial volume facilitates compression of more fluid per stroke than a smaller initial volume. As will be appreciated, the force sufficient to compress the fluid within thecompression cylinder 12 is at least partially dependent upon the initial fluid volume and the degree of fluid compression. Therefore, thestroke distance 96 and thediameter 98 of thepiston 36 may be particularly selected to provide the desired degree of compression, the desired flow rate through the reciprocatingcompressor 10, and the desired work applied by thepower source 16. -
FIG. 5 is a cross-sectional view of another embodiment of areciprocating compressor 10 having a piston configured to selectively block an intake port, and a flow control member configured to selective block a discharge port. As illustrated, thecompression cylinder 12 includes anintake port 100 and adischarge port 102. Theintake port 100 is fluidly coupled to aninlet 104 via aninternal passage 106 through thecompression cylinder 12. In operation, theinlet 104 receives a flow offluid 48, which is routed to theintake port 100 via theinternal passage 106. While theintake port 100 is fluidly coupled to theinlet 104 via aninternal passage 106 in the illustrated embodiment, it should be appreciated that alternative embodiments may utilize an external passage, or a combination of internal and external passages, to couple theinlet 104 to theintake port 100. - In the illustrated embodiment, the
discharge port 102 is fluidly coupled to anoutlet 108 via aninternal passage 109. As discussed in detail below, thecompressor 10 expels compressedfluid 56 through thedischarge port 102. The fluid then flows through theinternal passage 109 to theoutlet 108. While thedischarge port 102 is fluidly coupled to theoutlet 108 via aninternal passage 109 in the illustrated embodiment, it should be appreciated that alternative embodiments may utilize an external passage, or a combination of internal and external passages, to couple theoutlet 108 to thedischarge port 102. In the illustrated embodiment, theinlet 104 and theoutlet 108 are directed outwardly from thecompression cylinder 12 in theradial direction 64. Accordingly, substantially straight conduits may be coupled to theinlet 104 and to theoutlet 108, thereby enhancing flow efficiency, as compared to configurations that employ bent conduits coupled to axial ends of thecompression cylinder 12. In the illustrated embodiment, theoutlet 108 is positioned on the top of thecompression cylinder 12, and theinlet 104 is positioned on the bottom of thecompression cylinder 12. However, it should be appreciated that theinlet 104 may be positioned on the top, and theoutlet 108 may be positioned on the bottom. In such embodiments, theintake port 100 may be positioned above thedischarge port 102 within thecompression cylinder 12. Such a configuration may facilitate enhanced flow through thecompression cylinder 12 incompressors 10 having an inlet pipe positioned above thecylinder 12, and a discharge pipe positioned below thecylinder 12. - In the illustrated embodiment, the
piston assembly 20 includes thepiston 36, and aflow control member 110 extending from thepiston 36 in theaxial direction 60. Theflow control member 110 may be integral with thepiston 36 and/or thepiston rod 38, or coupled to thepiston 36 and/or the piston rod 38 (e.g., via fasteners, a welded connection, etc.). As discussed in detail below, theflow control member 110 is configured to block thedischarge port 102 during at least a portion of an intake stroke, and thepiston 36 is configured to block theintake port 100 during at least a portion of a compression stroke. In this manner, the reciprocatingcompressor 10 may cyclically receive a flow of fluid from theinlet 104, compress the fluid within thecompression cylinder 12, and expel the compressed fluid through theoutlet 108. - In the illustrated embodiment, the
piston 36 is configured to block theintake port 100 as thepiston 36 is driven in thedirection 84, thereby establishing a substantially sealedvolume 70 that facilitates fluid compression. To provide the substantially sealedvolume 70, thepiston assembly 20 includes afirst seal 112 disposed within arecess 113 in anexterior surface 114 of thepiston 36. Thefirst seal 112 is configured to substantially block fluid flow between theexterior surface 114 of thepiston 36 and aninterior surface 116 of thecompression cylinder 12. In addition, thepiston assembly 20 includes asecond seal 118 disposed within arecess 119 in theinterior surface 116 of thecompression cylinder 12. Similar to thefirst seal 112, thesecond seal 118 is configured to substantially block fluid flow between theexterior surface 114 of thepiston 36 and theinterior surface 116 of thecompression cylinder 12. As will be appreciated, theseals seals first seal 112, or the second seal 118) to substantially block fluid flow between theexterior surface 114 of thecylinder 36 and theinterior surface 116 of thecompression cylinder 12. - In the illustrated embodiment, the
flow control member 110 includes aprotrusion 120 extending radially outward from theflow control member 110. Theradial protrusion 120 is configured to block thedischarge port 102 while theradial protrusion 120 is aligned with thedischarge port 102. To provide the substantially sealedvolume 70, thepiston assembly 20 includes aseal 122 configured to substantially block fluid flow between anexterior surface 124 of theradial protrusion 120 and aninterior surface 126 of thecompression cylinder 12. As will be appreciated, theseal 122 may include a Babbitt seal, a labyrinth seal, a brush seal, and/or a ring seal, for example. While the illustratedseal 122 is disposed within arecess 127 in theinterior surface 126 of thecompression cylinder 12, it should be appreciated that theseal 122 may be disposed within a recess in theexterior surface 124 of theradial protrusion 120 in alternative embodiments. - The illustrated
reciprocating compressor 10 also includes apacking seal 128 disposed about theradial protrusion 120, and configured to substantially block fluid flow out of thecompression cylinder 12. While twoseals exterior surface 124 of theradial protrusion 120 and theinterior surface 126 of thecompression cylinder 12. In the illustrated embodiment, thepiston 36, theflow control member 110, theradial protrusion 120, and theseals piston 36, theflow control member 110, theradial protrusion 120, and theseals - In operation, the
piston assembly 20 is configured to compress fluid within thecompression cylinder 12 via cyclical movement in theaxial direction 60. For example, as thepiston assembly 20 is driven to move in thedirection 84, thepiston 36 moves across theintake port 100, thereby blocking fluid flow into theinterior volume 70. While theradial protrusion 120 is aligned with thedischarge port 102, a substantially sealedvolume 70 is established. As thepiston assembly 20 continues to translate in thedirection 84, the size of the substantially sealedvolume 70 decreases as thepiston 36 is driven toward an interioraxial surface 129 of thecompression cylinder 12. Accordingly, the pressure of the fluid within the substantially sealedvolume 70 progressively increases. Once theradial protrusion 120 is offset from thedischarge port 102, and a reducedradius portion 130 of theflow control member 110 is aligned with thedischarge port 102, a flow path is established that facilities flow of compressed fluid through thedischarge port 102 toward theoutlet 108. - Once the
piston assembly 20 has reached the end of the compression stroke, thepiston assembly 20 is driven in the oppositeaxial direction 80 to facilitate additional fluid flow into theinterior volume 70. For example, as thepiston assembly 20 is driven to move in theaxial direction 80, theradial protrusion 120 aligns with thedischarge port 102. As a result, fluid flow through thedischarge port 102 is substantially blocked. Furthermore, while thepiston 36 blocks theintake port 100, a substantially sealedvolume 70 is established. As thepiston assembly 20 continues to translate in thedirection 80, the size of the substantially sealed volume increases as thepiston 36 is driven away from the interioraxial surface 129 of thecompression cylinder 12. Accordingly, the pressure of the fluid remaining within the substantially sealedvolume 70 progressively decreases. Once thepiston 36 is offset from theintake port 100, the reduced fluid pressure within theinterior volume 70 draws additional fluid 48 from theinlet 104 through theintake port 100 and into theinternal volume 70. Once thepiston assembly 20 reaches the end of the intake stroke, thepiston assembly 20 is driven in the oppositeaxial direction 84, and the process repeats. - Because the
intake port 100 and thedischarge port 102 are selectively blocked by thepiston assembly 20, valves (e.g., check valves), which may otherwise be used to control fluid flow, are obviated. As a result, operational costs associated with valve maintenance may be substantially reduced or eliminated. In addition, because thepiston assembly 20 does not interfere with flow through theports reciprocating compressor 10 may be significantly enhanced, as compared to configurations that employ valves which may partially block the ports while in the open position. For example, certain reciprocating compressors include check valves to control fluid flow through the intake and discharge ports. In such configurations, each valve is biased toward a closed position by a spring. When a pressure differential exerts a force on the valve greater than the spring bias, a poppet is lifted off a seat, thereby facilitating fluid flow through the valve. However, the flow area through the open valve is limited by the valve lift height. In addition, the fluid flow is turned approximately 90 degree as the fluid approaching the valve is directly laterally outward via contact with the poppet. As a result of the limited flow area and the turned flow, the pressure of the compressed fluid may drop as the fluid flows through the valve, thereby decreasing compressor efficiency. In contrast, because the illustrated embodiment obviates the valves, fluid may flow through theports reciprocating compressor 10. -
FIG. 6 is a cross-sectional view of the reciprocating compressor ofFIG. 5 , illustrating movement of thepiston assembly 20 relative to thecompression cylinder 12. In the illustrated embodiment, the reciprocatingcompressor 10 includes a double-actingpiston assembly 20 configured to compress fluid within afirst side 133 of thecompression cylinder 12, while receiving fluid into asecond side 135 of thecompression cylinder 12. In this configuration, movement of thepiston assembly 20 in theaxial direction 84 compresses fluid within thefirst side 133 of thecompression cylinder 12, and receives fluid into thesecond side 135 of thecompression cylinder 12. Conversely, movement of thepiston assembly 20 in the oppositeaxial direction 80 compresses fluid within thesecond side 135 of thecompression cylinder 12, and receives fluid into thefirst side 133 of thecompression cylinder 12. As illustrated, thepiston assembly 20 includes two flow control members configured to control fluid flow within respective volumes of thecompression cylinder 12. The firstflow control member 110 is configured to control fluid flow within afirst volume 131 adjacent to afirst side 132 of thepiston 36. Similarly, a secondflow control member 134 is configured to control fluid flow within asecond volume 136 adjacent to asecond side 138 of thepiston 36. - In the illustrated embodiment, the second
flow control member 134 is driven to move by thepiston 36. Consequently, as thepiston rod 38 induces thepiston 36 to move in theaxial direction 80, the secondflow control member 134 is driven to move in theaxial direction 80. Conversely, as thepiston rod 38 induces thepiston 36 to move in theaxial direction 84, the secondflow control member 134 is driven to move in theaxial direction 84. As illustrated, the secondflow control member 134 is disposed within acap assembly 140, which is coupled to the compression cylinder 12 (e.g., via fasteners). Thecap assembly 140 includes a secondinternal passage 109 extending from asecond discharge port 102 to theoutlet 108. Thecap assembly 140 also includes afirst seal 142 and a second seal 144 disposed on opposite axial sides of thesecond discharge port 102. Similar to theseals seals 142 and 144 are configured to block fluid flow through thedischarge port 102 while theradial protrusion 120 of the secondflow control member 134 is aligned with thedischarge port 102. As will be appreciated, theseals 142 and 144 may include a Babbitt seal, a labyrinth seal, a brush seal, and/or a ring seal, for example. - In operation, as the
piston assembly 20 moves in thedirection 84, thepiston 36 successively blocks theintake port 100, and compresses fluid within thefirst volume 131. Theradial protrusion 120 of the firstflow control member 110 then moves out of alignment with thedischarge port 102, thereby facilitating fluid flow through thedischarge port 102. In addition, thepiston 36 successively drives the secondflow control member 134 to block thesecond discharge port 102, decreases fluid pressure within thesecond volume 136, and facilitates fluid flow through thesecond intake port 100 into thesecond volume 136. Conversely, as thepiston assembly 20 moves in thedirection 80, the firstflow control member 110 successively blocks thedischarge port 102, drives thepiston 36 to decrease fluid pressure within thefirst volume 131, and drives thepiston 36 out of alignment with the intake port, thereby facilitating flow of additional fluid into thefirst volume 131. In addition, thepiston 36 successively blocks thesecond intake port 100, compresses fluid within thesecond volume 136, and drives theradial protrusion 120 of the secondflow control member 134 out of alignment with thedischarge port 102, thereby facilitating fluid flow through thedischarge port 102. Because the reciprocatingcompressor 10 outputs compressed fluid with each stroke, the flow rate of compressed fluid may be greater than compressors employing single-acting piston assemblies having a single flow control member. While the illustrated embodiment employs a double-actingpiston assembly 20 to provide an increased flow of compressed fluid, it should be appreciated that alternative embodiments may employ single-acting piston assemblies. - As illustrated, the
piston 36 is aligned with theintake port 100, thereby blocking flow through theintake port 100, and establishing a substantially sealedvolume 131. As thepiston assembly 20 translates in thedirection 84, the size of the substantially sealedvolume 131 decreases as thepiston 36 is driven toward the interioraxial surface 129 of thecompression cylinder 12. In the illustrated embodiment, the stroke of thepiston rod 38 drives thepiston 36 to translate adistance 146, thereby decreasing the size of the substantially sealedvolume 131 by an amount equal to the cross-sectional area of an outerradial portion 147 of thepiston 36 multiplied by thestroke distance 146. As the volume decreases, the pressure of the fluid within the substantially sealedvolume 131 progressively increases. Once the reducedradius portion 130 of theflow control member 110 aligns with thedischarge port 102, thepressurized fluid 56 flows through thedischarge port 102 toward theoutlet 108. - As will be appreciated, the change in size of the substantially sealed
volume 131 is at least partially dependent on thestroke distance 146, and adiameter 148 of thepiston 36. For example, increasing thestroke distance 146 provides a greater change in the fluid volume, thereby increasing compression. Conversely, decreasing thestroke distance 146 provides a reduced change in the fluid volume, thereby decreasing compression. Furthermore, apiston 36 having alarger diameter 148 establishes a larger sealedvolume 131, while apiston 36 having asmaller diameter 148 establishes a smaller sealedvolume 131. The initial size of the sealed volume defines the fluid volume prior to compression. Consequently, a larger initial volume compresses more fluid per stroke than a smaller initial volume. As will be appreciated, the force sufficient to compress the fluid within thecompression cylinder 12 is at least partially dependent upon the initial fluid volume and the degree of fluid compression. Therefore, thestroke distance 146 and thediameter 148 of thepiston 36 may be particularly selected to provide the desired degree of compression, the desired flow rate through the reciprocatingcompressor 10, and the desired work applied by thepower source 16. -
FIG. 7 is a cross-sectional view of a further embodiment of a reciprocating compressor having a piston configured to selectively block an intake port and a discharge port. As illustrated, thecompression cylinder 12 includes anintake port 150 and adischarge port 152. As discussed in detail below, thepiston 36 is configured to block theintake port 150 during at least a portion of a compression stroke, and to block thedischarge port 152 during at least a portion of an intake stroke. In this manner, the reciprocatingcompressor 10 may cyclically receive a flow of fluid through theintake port 150, compress the fluid within thecompression cylinder 12, and expel the compressed fluid through thedischarge port 152. - In the illustrated embodiment, the
piston 36 includes aninternal passage 154 extending from theinterior volume 70 of thecompression cylinder 12 to anorifice 156 in anexterior surface 157 of thepiston 36. As discussed in detail below, thepiston 36 is configured to block thedischarge port 152 while theorifice 156 is offset from thedischarge port 152. Conversely, when theorifice 156 is aligned with thedischarge port 152, theinternal passage 154 establishes a flow path from theinterior volume 70 to thedischarge port 152, thereby facilitating flow of compressed fluid through thedischarge port 152. In the illustrated embodiment, thepiston 36 is an annular structure. However, it should be appreciated that thepiston 36 may be other shapes (e.g., rectangular, polygonal, etc.) in alternative embodiments. - In operation, the
piston assembly 20 is configured to compress fluid within thecompression cylinder 12 via cyclical movement in theaxial direction 60. For example, as thepiston assembly 20 is driven to move in theaxial direction 84, thepiston 36 blocks theintake port 150, thereby blocking fluid flow into theinterior volume 70. While theorifice 156 is not aligned with thedischarge port 152, a substantially sealedvolume 158 is established, which includes theinterior volume 70 and theinternal passage 154. As thepiston assembly 20 continues to translate in thedirection 84, the size of the substantially sealedvolume 158 decreases as thepiston 36 is driven toward aninterior surface 159 of theinternal volume 158. Accordingly, the pressure of the fluid within the substantially sealedvolume 158 progressively increases. Once theorifice 156 aligns with thedischarge port 152, the pressurized fluid is expelled through thedischarge port 152. - Once the
piston assembly 20 has reached the end of the compression stroke, thepiston assembly 20 is driven in the oppositeaxial direction 80 to facilitate additional fluid flow into theinterior volume 158. For example, as thepiston assembly 20 is driven to move in theaxial direction 80, theorifice 156 becomes offset from thedischarge port 152. As a result, thepiston 36 substantially blocks fluid flow through thedischarge port 152. Furthermore, while thepiston 36 blocks theintake port 150, a substantially sealedvolume 158 is established, which includes theinterior volume 70 and theinternal passage 154. As thepiston assembly 20 continues to translate in thedirection 80, the size of the substantially sealedvolume 158 increases as thepiston 36 is driven away from theinterior surface 159 of theinternal volume 158. Accordingly, the pressure of the fluid remaining within the substantially sealedvolume 158 progressively decreases. Once thepiston 36 is offset from theintake port 150, the reduced fluid pressure within theinterior volume 158 draws additional fluid through theintake port 150 and into theinternal volume 158. Once thepiston assembly 20 reaches the end of the intake stroke, thepiston assembly 20 is driven in the oppositeaxial direction 84, and the process repeats. - In the illustrated embodiment, the reciprocating
compressor 10 includes a double-actingpiston assembly 20 configured to compress fluid within afirst side 161 of thecompression cylinder 12, while receiving fluid into asecond side 163 of thecompression cylinder 12. In this configuration, movement of thepiston assembly 20 in theaxial direction 84 compresses fluid within thefirst side 161 of thecompression cylinder 12, and receives fluid into thesecond side 163 of thecompression cylinder 12. Conversely, movement of thepiston assembly 20 in theaxial direction 80 compresses fluid within thesecond side 163 of thecompression cylinder 12, and receives fluid into thefirst side 161 of thecompression cylinder 12. As illustrated, the reciprocatingcompressor 10 includes afirst volume 158 adjacent to afirst side 160 of thepiston 36. Thefirst volume 158 is defined by thecompression cylinder 12, thepiston 36, and anend cap 162 coupled to the compression cylinder 12 (e.g., via fasteners). In addition, the reciprocatingcompressor 10 includes asecond volume 164 adjacent to asecond side 166 of thepiston 36. Thesecond volume 164 is defined by thecompression cylinder 12, thepiston 36, and anend cap 168 coupled to the compression cylinder 12 (e.g., via fasteners). - In operation, as the
piston assembly 20 moves in thedirection 84, thepiston 36 successively blocks theintake port 150, and compresses fluid within thefirst volume 158. Once theorifice 156 is aligned with thedischarge port 152, compressed fluid flows through theinternal passage 154, and is expelled through thedischarge port 152. In addition, thepiston 36 successively blocks thesecond discharge port 152, decreases fluid pressure within thesecond volume 164, and unblocks thesecond intake port 150 to facilitate flow of additional fluid into thesecond volume 164. Conversely, as thepiston assembly 20 moves in thedirection 80, thepiston 36 successively blocks thefirst discharge port 152, decreases fluid pressure within thefirst volume 158, and unblocks thefirst intake port 150 to facilitate flow of additional fluid into thefirst volume 158. In addition, thepiston 36 successively blocks thesecond intake port 150, and compresses fluid within thesecond volume 164. Once asecond orifice 170 is aligned with thesecond discharge port 152, compressed fluid flows through a secondinternal passage 172, and is expelled through thesecond discharge port 152. Because the reciprocatingcompressor 10 outputs compressed fluid with each stroke, the flow rate of compressed fluid may be greater than compressors employing single-acting piston assemblies. While the illustrated embodiment employs a double-actingpiston assembly 20 to provide an increased flow of compressed fluid, it should be appreciated that alternative embodiments may employ single-acting piston assemblies. - In the illustrated embodiment, the
piston 36 includes arecess 174 and apassage 176 configured to receive apiston rod 38. In certain embodiments, thepiston rod 38 extends through theend cap 162, thereby enabling thepiston rod 38 to drive thepiston 36 in theaxial directions piston rod 38 to block fluid flow out of thecompression cylinder 12. Furthermore, it should be appreciated that additional seals may be disposed throughout the reciprocatingcompressor 10. For example, seals may be positioned on opposite axial ends of theorifices discharge ports 152 until each orifice is aligned with a respective port. In addition, seals may be disposed about theintake ports 150 to block fluid flow through each intake port while thepiston 36 is aligned with a respective intake port. - Because the
intake port 150 and thedischarge port 152 are selectively blocked by thepiston 36, valves (e.g., check valves), which may otherwise be used to control fluid flow through theports piston assembly 20 does not interfere with flow through theports reciprocating compressor 10 may be significantly enhanced, as compared to configurations that employ valves which may partially block the ports while in the open position. Furthermore, theinternal passages piston 36 may substantially reduce the reciprocating mass of thecompressor 10, thereby reducing the energy utilized to drive thepiston assembly 20 to move in theaxial directions reciprocating compressor 10 may be enhanced, as compared to configurations employing solid pistons. -
FIG. 8 is a cross-sectional view of the reciprocating compressor ofFIG. 7 , illustrating movement of thepiston assembly 20 relative to thecompression cylinder 12. As illustrated, thepiston 36 is aligned with theintake port 150, thereby establishing a substantially sealedvolume 158. As thepiston assembly 20 translates in thedirection 84, the size of the substantially sealedvolume 158 decreases as thepiston 36 is driven toward theinterior surface 159 of theinternal volume 158. In the illustrated embodiment, the stroke of thepiston rod 38 drives thepiston 36 to translate adistance 178, thereby decreasing the size of the substantially sealedvolume 158 by an amount equal to the cross-sectional area of thepiston 36 multiplied by thestroke distance 178. As the volume decreases, the pressure of the fluid within the substantially sealedvolume 158 progressively increases. Once theorifice 156 aligns with thedischarge port 152, the pressurized fluid is expelled through thedischarge port 152. - As will be appreciated, the change in size of the substantially sealed
volume 158 is at least partially dependent on thestroke distance 178, and adiameter 180 of thepiston 36. For example, increasing thestroke distance 178 provides a greater change in the fluid volume, thereby increasing compression. Conversely, decreasing thestroke distance 178 provides a reduced change in the fluid volume, thereby decreasing compression. Furthermore, apiston 36 having alarger diameter 180 establishes a larger sealed volume, while apiston 36 having asmaller diameter 180 establishes a smaller sealed volume. The initial size of the sealed volume defines the fluid volume prior to compression. Consequently, a larger initial volume compresses more fluid per stroke than a smaller initial volume. As will be appreciated, the force sufficient to compress the fluid within thecompression cylinder 12 is at least partially dependent upon the initial fluid volume and the degree of fluid compression. Therefore, thestroke distance 178 and thediameter 180 of thepiston 36 may be particularly selected to provide the desired degree of compression, the desired flow rate through the reciprocatingcompressor 10, and the desired work applied by thepower source 16. - While the invention may be susceptible to various modifications and alternative forms, specific embodiments have been shown by way of example in the drawings and have been described in detail herein. However, it should be understood that the invention is not intended to be limited to the particular forms disclosed. Rather, the invention is to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the invention as defined by the following appended claims.
Claims (20)
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/354,263 US9435322B2 (en) | 2012-01-19 | 2012-01-19 | Valveless reciprocating compressor |
EP12791323.4A EP2820296A1 (en) | 2012-01-19 | 2012-10-23 | Valveless reciprocating compressor |
PCT/US2012/061497 WO2013109326A1 (en) | 2012-01-19 | 2012-10-23 | Valveless reciprocating compressor |
CN201280071610.XA CN104520584B (en) | 2012-01-19 | 2012-10-23 | Valveless reciprocating compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/354,263 US9435322B2 (en) | 2012-01-19 | 2012-01-19 | Valveless reciprocating compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
US20130189139A1 true US20130189139A1 (en) | 2013-07-25 |
US9435322B2 US9435322B2 (en) | 2016-09-06 |
Family
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Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/354,263 Active 2033-04-28 US9435322B2 (en) | 2012-01-19 | 2012-01-19 | Valveless reciprocating compressor |
Country Status (4)
Country | Link |
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US (1) | US9435322B2 (en) |
EP (1) | EP2820296A1 (en) |
CN (1) | CN104520584B (en) |
WO (1) | WO2013109326A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112081729A (en) * | 2020-08-18 | 2020-12-15 | 华南农业大学 | Resonant piezoelectric stack pump with slide valve |
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US2495445A (en) * | 1946-01-12 | 1950-01-24 | William F Crenshaw | Double piston valveless pump or engine |
DE2006824A1 (en) * | 1970-02-14 | 1971-08-26 | Stelzer, Frank 6450 Hanau | Reciprocating compressor |
US3991574A (en) * | 1975-02-03 | 1976-11-16 | Frazier Larry Vane W | Fluid pressure power plant with double-acting piston |
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US20100303656A1 (en) * | 2008-04-30 | 2010-12-02 | Bo Lin | Metering pump and drive device thereof |
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GB149890A (en) | 1920-02-28 | 1920-08-26 | Percy Pritchard | Improvements in or relating to air or like compressors |
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GB1470597A (en) | 1974-08-21 | 1977-04-14 | Sterling Winthrop Group Ltd | Reciprocating pumps for dispensing pastes liquids and other substances |
US8172799B2 (en) | 2007-01-10 | 2012-05-08 | Acist Medical Systems, Inc. | Volumetric pump |
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2012
- 2012-01-19 US US13/354,263 patent/US9435322B2/en active Active
- 2012-10-23 CN CN201280071610.XA patent/CN104520584B/en active Active
- 2012-10-23 WO PCT/US2012/061497 patent/WO2013109326A1/en active Application Filing
- 2012-10-23 EP EP12791323.4A patent/EP2820296A1/en not_active Withdrawn
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US2296647A (en) * | 1941-02-28 | 1942-09-22 | Racine Tool & Machine Company | Hydraulic pressure booster |
US2495445A (en) * | 1946-01-12 | 1950-01-24 | William F Crenshaw | Double piston valveless pump or engine |
DE2006824A1 (en) * | 1970-02-14 | 1971-08-26 | Stelzer, Frank 6450 Hanau | Reciprocating compressor |
US3991574A (en) * | 1975-02-03 | 1976-11-16 | Frazier Larry Vane W | Fluid pressure power plant with double-acting piston |
US4286929A (en) * | 1977-03-23 | 1981-09-01 | Rodney T. Heath | Dual pressure gas motor, and method of operation |
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US20060090477A1 (en) * | 2002-12-12 | 2006-05-04 | Leybold Vakuum Gmbh | Piston compressor |
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US20100303656A1 (en) * | 2008-04-30 | 2010-12-02 | Bo Lin | Metering pump and drive device thereof |
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CN112081729A (en) * | 2020-08-18 | 2020-12-15 | 华南农业大学 | Resonant piezoelectric stack pump with slide valve |
Also Published As
Publication number | Publication date |
---|---|
CN104520584A (en) | 2015-04-15 |
WO2013109326A1 (en) | 2013-07-25 |
CN104520584B (en) | 2017-09-15 |
EP2820296A1 (en) | 2015-01-07 |
US9435322B2 (en) | 2016-09-06 |
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